Winding machine



S pt 17, 1929- CH. JONES ETAL WINDING MACHINE 5 Sheets-Sheet Filpd Feb. 13 1928 Sept. 17, 1929- c. H. JONES ET AL 1 ,728,413

' WINDING MACHINE Filed Feb. 13, 1928 5 Sheets-sheet 2 Sept; 17, 1929. c. H. JONES ErAL WINDING MACHINE Filed Feb. 13 1928 5 Sheets-Sheet 3 P 1929- c. H. JONES ET AL "1,728,413

WINDING MACHINE Filed Feb. 13. 1928 v 5 Sheets-Sheet 4 Sept. 17, I929.

C. H. JONES ET AL WINDING MACHINE Filed Feb. 1'3 1928 5 Sheets-Sheet Patented Se t. 17, 1929 UNITED STATES PATENT OFFICE CHARLES H. JONES, OF PROVIDENCE, AND ERNEST R. SY'VANSON, OF CRANSTON,

RHODE ISLAND, ASSIGNORS TO UNIVERSAL WINDING COMPANY, OF BOSTON, MAS- SACHUSETTS, A CORPORATION OF MASSACHUSETTS i WINDING MACHINE Application filed February 13, 1928. Serial No. 254,047.

This invention relates to improvements in winding machines for winding cops, cones and packages of thread, yarn, cord and other strand material, and particularly to winding machines wherein the cop or package is rotated from contact with a drive-roll or drum. The invention contemplates the provision of a ribbon-breaking device for controlling the lay of the strand on the package to prevent the formation of bands or ribbons caused by the coils of winding becoming crowded together.

A principal object of the invention is to provide means incorporated in the drivingmechanism of the winding machine which functions to break or disrupt the synchrony of operation between the cop-holder and the thread-guide whereby to regulate the disposition of the helical coils of yarn or the like throughout the winding of the cop or package.

Another object of the invention is to provide a device of the type specified wherein the traversing speed of the thread-guide is accelerated and correspondingly retarded in recurring cycles during the winding.

Another object of the invention is to provide a device of the type specified in which the variation in speed of the thread-guide is accomplished by shifting one element of the driving gears circumferentially of a second element of the drive through the means of a simple crank-motion or cam-operated device.

Another object of the invention is to provide a device of the type specified which is entirely automatic in its functioning and requires no adjustment previous to the winding operation.

Another object of the invention is to provide a device of the type specified which may be embodied in the driving-mechanism of the winding machine without unduly com plicating the arrangement thereof or materially increasing the number of parts therein.

Further objects of the improvement are sett'orth in the following specification which describes a preferred form of construction of the invention by way of example as illustrated by the accompanying drawings. In the drawings: I

Fig. 1 is an end view of a winding machine 01 the double gang type, showing the essential elements of the winding mechanism comprising the cop-holder, the drive-roll for rotating the cop, the thread-guide for traversing the strand material on the cop, the cam for reciprocating the thread-guide and illustrating the present improved ribbonbreaker or speed-changing device as applied to use therewith;

Fig. 2 is a side view of the gang machine showing the winding elements for one unit and illustrating the driving-mechanism with its gearing in section on line 22 of Fig. 1;

Fig. is a detailed view of the gearing for the driving-mechanism as viewed in a direc tion opposite to that in Fig. 1; i

Fig. 4 is a further detailed view of the gearing and the associated crank-motion for i the ribbon-breaker;

Fig. 5 is a similar view showing the parts in difierent relation;

6 is a detailed view of the crankmotion showing the partsin section on line 66 of Fig. 3; and

Fig. 7 is a view showing a modified form of means for operating the differential motion for the gearing.

The present invention resides particularly in means for imparting an alternately accelerated and retarded rate of speed to one of the co-operative winding elements of the machine, either the drive-roll which rotates the cop 'or package or the thread-guide which traverses the yarn thereon, such means being embodied in differential gearing operated from a crank-motion or the equivalent and forming a part of the drive'for the machine. i

Referring to the drawings, the winding machine herein illustrated by way of example is of the double gang type having two series of winding units arranged in opposite relation along the sides of a frame or bed, not herein shown, which is supported from the usual legs or standards. Fig. 1 illustrates this arrangement of the opposite winding units in end view and Fig. 2 shows a side view of one unit only, the other units being duplicates thereof and of any number in accordance with requirements. In Figs. 1 and 2 the driving-rolls or drums D and D are shown as being mounted on and tated from a pair of horizontal shafts 2 and 3 having their ends journalled in suitable bearings at opposite ends of the frame or bed. Referring to Fig. 2, one end of each shaft 2 and 3 is journalled in ball-bearings a in two'opposite tramamembers or uprights 5 and 6 which are supported from the main -frame or bed of the machine; a third "frame-member or upright, not herein shown, being provided at the opposite end of the bed for mounting similar bearings for the other ends of the two shafts.

Also journalled in. bearings in the endframes and arranged below the shafts 2 and 3 are two parallel horizontal shaiits 7 and 8 for ro'tatably supporting and driving the traverse-cams C and C.

The cams C, C are of usual form comprising skeleton rims having helical grooves c therein for engaging with a bowl or roller 9 which connect the cams to reciprocate the traversing thread-guides T. The threadguides T may comprise a sleeve 10 slidably mounted on a horizontal rod or bar 11 and carrying an upright, curved arm provided with a slot or groove 25 in its head for receiving the strand of yarn, thread or other material.

The rotatable support or windingspindle for the cop,- cone or package may be of any usual construction suitably mounted to adapt it to contact with the drive-roll D and to recede therefrom as the winding is built up on the cop-holder. The cop-holder usually consists of a paper shell or tube and in the present drawings is illustrated in the term of a cone-tube X for receiving and supporting a conical package. The means for supporting the winding-spindle or copholder in driving relation with respect to the drive roll is not herein illustrated as it may be oi any well-known construction as commonly used inthe art. The other details of the winding unit are alsoomitted in the present drawings since they may be of usual construction and arrangement, it being sufficient for an understanding of the present improvement to note that the driverolls 1), D are rotated in opposite directions, as indicated by the arrows in Fig. l, to cause the cop-holders to be driven therefrom to wind the strand material thereon as the thread-guides T, T" are reciprocated longitudinally of the drive-rolls through their connections with the cams C, C and thus caused to transverse the yarn to dispose it in coils or turns wound helically of the cops.

In frict1on-- or drum-driven winding Inachines of the present type the speed o't rotation of the drive-roll is constant and the ro tative speed of the cop or package is therefore gradually reduced during the winding due to the increase in the circumference of the cop during its contact with the periphery of the drive-roll. Owing to this fact the character of the winding is constantly changing from start tofinish' of the package as caused by the disparity in operating speed between the package and the threaduide. Stated another way, the turns or the winding are disposed on the cop-holder at the start of the package in certain predetermined relation so that they cross and recross each other in winding from one end of the package to the other and lie open or with spaces between adjacent turns extending in the same direction. As the winding proceeds, however, the reduction in speed. of the cop causes the turns of the winding to be disposed in closer tionship until at a certain point they crowded together or piled with n laid substantially on top of anri hen this point has been reached turns or coils open up again, being thereafter spaced apart to an increasing extent, and. this process is repeated periodically throughout the winding. The'piling of the turns of the winding causes what is termed ribbon consisting oi? a band of closely wound turns bunched or crowded together i; a helical course around the pack ag This crowded condition of the coils ribbon e'flect on the surface of the package hampers or impedes free delivery of the material 111 unwinding the package as the close wound coils are restricted from uncoiiing or slipping oft over the end of the package, thus causing abnormal tension on the strand which weakens and in some instances causes breakage of the thread. Various methods have been heretofore suggest d for preventing ribbon winding on the sin-face of the package and the present invention contemplates the employment of an improved ribbon-breaker constituted in differential gearing which is embodied in the driving-mechanism oi? the machine. The construction and arrangement of this improved device will now be described in detail.

Fig. 2 of the drawings pulley 15 for transmitting shows a beltpower to the winding machine, the pulley being mounted fast on a short drive-shaft 16 which is journalled in suitable ball-bearings 17 in the two opposite frame-members 5 and 6, the outboard bearing 18 being supported from an arm 19 bolted to and forming an extension of the standard 6, see Fig. 6. Below the drive-shaft 16 is a countershaft 2O journalled in ball-bearings 21 mounted on the frame-members 5 and 6. The countershait 9.0 is connected to be driven from the shaft 16 at the same rate of speed through the means of equal gears '22 and 23 suitably keyed to their respective shafts. At the outer end of the drive-shaft 16 is a larger gear 24 suitably keyed thereto and meshing with a gear 25 on the drive-roll shaft 2, see Fig. 1. Agear 26 equal in diameter to the gear 24 is keyed to the right-hand end of the countershaft 20 with its teeth in mesh with a gear 27 on the other drive-roll shaft 3. Through these connections the shafts 2 and 3 for the series of drive-rolls D and D are driven in opposite directions and at the same rate of speed, it being noted that the drive-rolls are rotated in opposite directions to cause the strands of yarn g to feed from the thread-guides to the under side of the packages being wound.

In the present embodiment of the invention the drive-rolls or friction-drumsD and D are driven at a constant rate of speed and the differential drive is applied to the traverse-cams to accelerate and retard the reciprocatory speed of the threadguides T, T; but if preferred the arrange ment may be reversed and the differential speed-changing mechanism arranged to control the rotation of the drive-rolls. The first noted arrangement is usually preferred, however, and the method of applying the differential speed-changing device or ribbon-breaker to operate on the threadguides of the machine will next be described. i

The two series of cams C, C which reciprocate the thread-guides T, T are driven from the countershaft 20 through a train of gearing organized as follows: Below the countershaft 20 is a smaller parallel shaft 30 which is fixedly supported with its ends held in bearings 31 and 32 on the frame-members 5 and 6'. The bearing 31 is formed integral with the frame-member 5, whereas the opposite bearing 32 comprises a boss or hub formed as a part of a bracket 33 which is attached to the side of the foot of the bearing 6 by means of bolts 34, seeFig. 3. The bracket 33 has a downwardly extending arm 35 which is formed with a vertical slot 36 for connection with the crankmotion of the differential mechanism in the manner and for the purpose as later more fully explained. Referring again to Fig. 2, the shaft 30 is held from turning in its bearings by means of a set-screw 37 inserted through the side of the hub 32.

The countershaft 20 carries a pinion 40 held fast thereon by means of a tapered pin 39 and having its teeth in mesh with a gear 42. The gear 42 has its hub 43 forced onto the end of a sleeve or bushing 44 which is free to turn on the lower shaft 30. At one side of the gear 42 is a gear 45 of the same size which is also free to turn on the shaft 30. These two gears 42 and 45, which may be termed the drivingand driven-gears, turn in opposite directions, the gear 42 driving the gear 45 at varying speeds through a differential mechanism as next described. The gear 42 is driven from the pinion 40 on the countershaft 20 in the direction indicated by the arrows in Fig. 1, it being noted that Fig. l is a view looking in the direction indicated by the arrow :12 in Fig. 2, while Fig. 3 is a view looking in the opposite direction or from the right in Fig. 2. The gear 45 is driven from the gear 42 in the opposite direction through the means of twin pinions 46 and 47 organized therewith in a novel and peculiar manner as next ex.- plained.

The differential mechanism is shown in detail in Figs. 4 and 5 which are views looking in the same direction as in Fig. 3. The twin differential pinions 46 and 47 have their teeth meshing respectively with the gears 42 and 45 and mesh together to cause rota tion of gear 45 in the opposite direction from gear 42, Fig. 4 representing gear 45 at the rear of gear 42 and shaded dark for the sake of contrast. In Fig. 5 the gear 42 is removed to more clearly illustrate the drive to the gear 45 and from the gear 45 to the cam-shaft gears, these connections being as later described. The twin pinions 46 and 47 are journalled on a swinging yoke or frame 50 comprising opposite parallel arms 51 and 52 having hubs pivoted on the shaft 30. The hub 53 of the arm 51 is mounted on the shaft 30 between the hub of the gear 45 and the bearing 31; while the hub 54 of the arm 52 pivots on the bushing 44 in the hub 43 of the gear 42. Referring to Figs. 4, 5 and 6, the pinion 46 is free to rotate on a short shaft 55 held fixedly in bosses 56 and 57 forming an extension of the frame 50. The pinion 47 is rotatable on a'longer shaft 58 which is fixedly held in bosses 59 and 60 formed as a part of the frame 50, the shaft 58 projecting from the end of the bearing 60 as illustrated in Fig. 6. This end of the shaft 58 carries a crankgear 65, shown in section in Figs. 2 and 6 and illustrated in diagram in Figs. 4 and 5. The crank-gear is mounted free toturn on the shaft 58, being held in place by a collar 66 fastened to the shaft by a cotter-pin 67. The teeth on the gear 65 mesh with teeth out into the end of the hub 44 of the gear 43, the end of the hub thus serving as a pinion 65 for driving the crank-gear. The crank-gear 65 is provided with a crankpin 70 which projects from its side in position to engage with the vertical slot or trackway 36 in the fixed arm 35 which is rigidly attached to the frame-member 6 in the manner as previously described. It will thus be observed that as the crank-gear 65 is driven from the pinion 64 connected to the gear 42 its crank-pin 70 will play up and down in the slot 36 and through its engageinent therewith will rock the frame 50 back and forth on its axis in an arc defined by the eccentricity or extent of stroke of its crank pin, see Figs. 4 and 5' which illustrate the frame 50 at the two opposite extremes of its throw.

It has been stated that the pinion 46 is driven from the gear 42 to transmit motion to the pinion 47, and this latter pinion meshes with the gear 45 to turn it in the opposite direction from the gear 42, normally at the same rate of speed. Fig. 6 illustrates the arrangement of the meshing twin pinions 46 and 47 and discloses the manner in which these pinions interengage to turn in opposite directions with the opposite end portions of their teeth meshing respectively with the two spaced gears 42 and It will be seen by reference to this view that the pinion 46 has its teeth extended beyond the side of the gear 42 to adapt them tomesh throughout half the length of the teeth on the pinion 47. It will also be noted that .the pinion 46 is cutaway where it extends across the toothed face of the gear 45 and likewise the pinion 47 is cut away where it extends across the face of the gear 42. In other words, the two pinions are disposed so that their intermeshing teeth extend in opposite directions to engage the two gears 42 and 45 and their reduced projecting hub portions overlie the toothed faces of the opposite gears without interference therewith.

It now being. understood that the gear 45 is driven from the gear 42 through the differential pinions 46 and 47 which are oscillated circumferentially of these two gears the connections between the driven gear 45 and the cam-shafts 7 and 8 will next be explained. The gear 45 is directly connected to drive the series ofcams C by means of a gear 68 carried on the cam-shaft 8 and secured fast therewith by a set-screw 69. The opposite cam-shaft 7 is driven in the opposite direction from that of the camshaft 8- and therefore an idler gear 71 is interposed between the gear 45 and the camshaft gear 78. Referring to- Figs. 1 and 5 the gear 45 meshes with the idler 71 which is rotatably held on a stud 72 projecting from the side of the frame-member 5, see'also Fig. 2. The stud 72 may be bolted or otherwise suit-ably secured in a boss 7 3 on the framemember 5 and held by a nut 74-. The hub 7 5 of the idler 71 turns on a reduced portion of the stud 72 and is held in place by a collar 76 secured by a set-screw 77. The idler 71 engages directly with the gear 78 which is keyed to the cam-shaft 7 and secured by a set-screw 79.

Fig. 7 illustrates a modified form of mechanism for transmitting motion to the rockable frame 50 whereby to oscillate the differential pinions 46 and 47 circumferentially of the gears 42 and 45. In this embodiment of the invention a cam-gear 80 takes the place of the crank-gear 65 previously described. The gear 80 has a heartshaped cam rim 81 projecting from its side with its periphery bearing against a fixed lug or abutment 82 which projects from an arm 83 reaching down from a bracket 84 The bracket 84 is fixedly secured to the base of the frame-member 6 by bolts 85, thus replacing the bracket 33 used with the crank-motion. The cam 81 is thus caused to swing the frame 50 on the axis of the shaft 30 in the manner and for the purpose as previously explained.

The method of operation of the complete winding machine is as next explained. Power is applied to the machine through the means of the usual belt passing over the driving pulley to rotate the shaft 16. The shaft 2 for the series of drive-rolls D is driven directly from the drive-shaft 16 through gears 24 and 25, see Fig. 1, while the shaft 3 for the opposite series of driverolls D is driven at the same rate of speed from the gear 26 on the countershaft 2O meshing with gear 27. The drive-rolls D, D" are therefore driven at a constant rate of speed to transmit rotation to the copholders, herein illustrated as carrying conetubes X which are initially held with their surfaces in contact with the peripheries of the rolls. In preparing the machine for winding the strands are led through the slots t in the thread-guides T and their ends secured to the cop tubes X so that when. the machine is started the yarn or other material will be wound onto the tubes to build up the packages. As the cop-tubes are retated from the drive-rollsthe thread-guides T and T are traversed longitudinally thereof to dispose the strand material: in crosswound coils extending helically of the axes of the packages.

The two opposite series of thread-guides T and T are reciprocated from their ca ms C and C" which are rotated from the snafts 7 and 8. The cam-shafts 7 and 8 are driven in opposite directions from the countershaft through the medium of the differential gearing in the manner as next explained. The countcrshaft 2O drives the gear 42 from the pinion at a reduced rate of speed. The gear 42 drives the pinion 46 in the direction indicated by the arrow in Fig. 4 and rotationis thereby transmitted to the twin pinion 47 in the opposite direction. The pinion 47 meshes with the gear to drive the latter in the direction indicated by the arrows in Fig. 5 and rotation is transmitted from gear 45 through gear 68 to drive the cam-shaft 8. The opposite cam-shaft 7 is driven from the gear 45 through the medium of the idler 71 meshing with the gear 78. s

As the gear 45 is rotated from the countershaft 20 the pinion 64 on the end of its hub 44 turns the crank-gear 65 in the direction indicated by the arrow in Fig. 3. The crank-pin 7 0 is thus caused to play up and down in the slot or trackway 36 in the arm 35 to impart an oscillating motion to the rockable frame 50, whereby the twin pinions 46 and 47 are traveled back and forth in an arcuate path concentric with the axis of the shaft 30. As the pinion 46 is rolled around the circumference of the gear 42 in the direction indicated by the arrow at in Fig. 4, its speed of rotation will be increased due to the fact that its travel is in a direction opposite to that in which the gear 42 is turning. This increase in speed is transmitted through the pinion 47 to the drivengear 45 which will therefore have its speed proportionately increased, or, in other words, it will have an increment or gain in speed over that of the driving-gear 42. This increment in speed of the gear 45 will be communicated through the gears meshing therewith to rotate the two cam-shafts 7 and 8 at an accelerated speed whereby the reciprocatory motion of the thread-guides is correspondingly accelerated. Fig. 4 illustrates the frame 50 in its position of extreme movement to the left, while Fig. 5 illustrates the frame at the opposite extreme of its oscillating motion to the right of the vertical center of the gear 42.

After the frame 50 has reached the position shown in Fig. 5 isstarts to return to its opposite extreme of throw and as it moves in the direction indicated by the arrow I) the speed of the driven-gear 45 will be retarded. That is to say, as the pinion 46 rolls back around the circumference of the driving-gear 42 in the direction of rotation of this latter gear, see Fig. 4, its rotation will be retarded and consequently the drive through the pinion 47 to the gear 45 will be at a slower rate of speed. In this way the speed of the driven-gear 45 is alternately accelerated and retarded to effect a corresponding increase and decrease in the speed of rotation of the cams C and C. The thread-guides T and T will therefore be reciprocated at a constantly varying or differential rate of speed and as a result thereof the synchrony of operation between the guides and the winding-spindles or copholders will be disrupted. Due to this gradual and constant change in the speed relation between the thread-guides and the rotating cop-holders the tendency to lay the yarn on the cops in bands or ribbons will be eliminated and defects in the winding will thereby be prevented. Stated briefly, by disrupting the synchrony of operation between the rotating cop-holders and reciprocating thread-guides the differential mechanism acts as a ribbon-breaker to prevent the turns or coils of winding from approaching a point where they are crowded or laid in close juxtaposition to form bands or ribbons, as theresult where the motion of the thread-guides is synchronized with the rotation of the cop-holders.

It will be observed from the above that the invention provides a particularly simple and efficient differential speed-changing mechanism for the purpose explained. The differential gearing may be incorporated in the drive of the machine without unduly multiplying the number of parts or extending its mechanism. Moreover, the ribbonbreaking device requires no adjustment or setting of its parts, but functions automatically throughout the operation of the machine to prevent defects in the winding. It will be understood that where the modified form of oscillating-means for the differential pinions as shown in Fig. 7 is employed, the method of operation of the dea,

vice is the same as above explained.

Further modifications may be made in the construction and arrangement of the parts of the device without departing from the spirit or scope of theinvent-ion as defined connecting the driving-gear to drive the driven-gear, and means for oscillating the plnions about the axis of the driving-gear to shift their position circumferentially thereof to vary the speed of rotation transmitted to the driven-gear.

2. In a winding machine, the combination of a cop-holder, a drive-roll for rotating the cop-holder, means for traversing strand material on the cop-holder, driving-mechanism for rotating the drive-roll and actuating the traversing-means, and means in the drivingmechanism for disrupting the synchrony of operation between the drive-roll and traversing-means comprising a driving-gear, a

drivengear, intermeshing pinions driven from the driving-gear to transmit rotation to the driven-gear, means for supporting said pinions to adapt them to oscillate about the axis of the driven-gear, and a crankmotion driven wlth the driving-gear and connected to operate the pin ons to travel them back and forth circumferentially of the driving-gear.

8. In a winding machine, the combination of a cop-holder, a drive-roll for rotating the cop-holder, a thread-guide for traversing strand material on the cop-holder, driving-mechanism for rotating the drive-roll and effecting relative reciprocation between the cop-holder and thread-guide, and differential gearing incorporated in said driving-mechanism comprising a drivinggear, a driven-gear rotatable on the same axis with the driving-gear, a pinion driven from the driving-gear, a second pinion driven from the first pinion and connected to drive the driven-gear, and means for oscillating said pinions about a fixed axis to travel them back and forth circumferentially of their respective gears.

4. In a winding machine, the combination of a cop-holder, a drive-roll for rotating the cop-holder, *a thread-guide for traversing strand material on the copholder, drivingmechanism for rotating the drive-roll and effecting relatlve reciprocation of the threadguide, and differential gearing in the driving-mechanism for interrupting the synchrony of motion between the drive-roll and thread-guide comprising a driving-gear, a driven-gear, a pinion connected to be driven from the driving-gear, a second pinion driven from the first pinion and connected to drive the drivemgear in the opposite direction from that of the driving-gear, and means for traveling sald plnlons back and forth circumferentially of their respective gears to vary the speed ratio between the drl'ving gear and driven-gear 1n the manner and for the purpose substantially as described.

5. In a winding machine, the combination of a cop-holder, a drive-roll for rotating the cop-holder. means for traversing strand m'aterial-on the cop-holder, means for rotating the driveroll, and means for operating the for reciprocating the threadeguide, and

means for driving the cam with an alternately accelerated and retarded rate of speed comprising a driving-gear, a driven-gear, a pinion driven from the driving-gear, a second pinion driven therefrom and connected to drive the driven-gear, and automatically operated means for traveling the first pinion back and forth circumferentially of the driving-gear.

7. In a winding machine, the combination of a cop-holder, a drive-roll for rotating the cop-holder, a thread-guide for traversing strand material on the cop-holder, drivingmeans for rotating the drive-roll at a constant rate of speed, means for reciprocating the thread-guide, and means connecting the driving-means to operate the reciprocating means with a differential rate of speed comprising a driving-gear, a driven-gear, a pinion driven from the driving-gear, a second pinion driven therefrom and connected to drive the driven-gear, and automaticallyoperated means for continuously traveling the first pinion back and forth circumferentially of the driving-gear.

8. In a winding machine, the combination of a cop-holder, a drive-roll for rotating the cop-holder, means for traversing strand material on the cop-holder, driving-means for rotating the drive-roll, and differential gearing for connecting said driving-means to operate the traversing-means comprising a driving-gear, a driven-gear, a pinion driven from the driving-gear, a second pinion driven therefrom and connected to drive the drivengear, and antomatically-operated means for continuously oscillating the first pinion to travel it back and forth circumferentially of the driving-gear.

9. In a winding machine, the combination of a cop-holder, a drive-roll for rotating "the cop-holder, traversing-means for traversing strand material on the cop-holder, means for rotating the drive-roll, and means for operating the traversing-means comprising a driving-gear, a driven-gear, a pinion driven from the driving-gear, a second pinion driven therefrom and connected to drive the driven-gear, a crank-gear driven with the driving-gear and provided with a crank-pin, and a stationary trackway engaging the crank-pin to cause it to oscillate the first pinion to travel it back and forth circum- 'ferentially of the driving-gear to vary the speed ratio of the driven-gear.

10. In a winding machine, the combination of a cop-holder, a drive-"oil for rotat mesh with the first pinionand meshing with the driven-gear, a crankgear on said frame provided with a crank-pin, a pinion connected with the driving-gear for driving said crank-gear. and a fixed trackway engaging the crank-pin to cause the crank-gear to oscillate the frame to travel the pinions back and forth circumferentially of their respective gears.

11. In a winding machine, the combination of a cop-holder, a drive-roll for rotating the cop-holder, means for traversing strand material on the cop-holder, drivingmeans for rotating the cop-holder and op erating the traverse-means, and differential gearing in said driving-means comprising a driving-gear, a driven-gear rotatable on the same axis with the driving-gear, a frame pivoted on the axis of the drivingand driven-gears, a pinion journalled on said frame in mesh with the driving-gear, a second pinion journalled on the frame in mesh with the first pinion and meshing with the driven-gear to drive the latter in the oppo site direction from that of the driving-gear, and means for oscillating the frame to travel the pinions back and forth circumferentially of their respective gears to vary the speed ratio between the driving-gear and driven-gear.

12. In a winding machine, the combination of a cop-holder, a drive-rol for rotating the cop-holder, traversing-means for traversing strand material on the copholder, and differential gearing for varying the speed ratio between the drive-roll and traversing-means comprising a driving-gear, a driven-gear rotatable on the same axis with the driving-gear and spaced laterally therefrom, a frame pivoted to rock on the axis of said gears, a pinion jonrnalled on said frame in mesh with the driving-gear and extending to one side thereof, a second pinion journalled on the frame in mesh with the first pinion and also meshing with the driven-gear, and means to oscillate the frame to travel said portions circumferentially of their respective gears to vary the speed ratio between the driving-gear and the driven-gear.

13. A ribbon-breaking device for winding machines comprising a shaft, a driving-gear rotatable on said shaft, means for driving said gear at a constant rate of speed, a driven-gear rotatable on the shaft at one side of the driving-gear, a frame pivoted to rock on said shaft, a pinion journalled on said frame with its teeth in mesh with the driving-gear and extending laterally with respect thereto, a second pinion journalled on the frame with its teeth meshing with the first pinion at one side of the driving-gear and also meshing with the driven-gear, a pinion rotatable with the drivingear, a crank-gear j ournalled on the frame in mesh with the last named pinion and carrying a crank-pin, and a slotted member engaging the crank-pin to cause the crank-gear to oscillate the frame to travel the interengaging pinions circumferentially of their respective gears.

14. In a ribbon-breaking device for winding machines, the combination of a shaft, a driving-gear free to turn on said shaft, a driven-gear free to turn on the shaft at one side of the driving-gear, a frame pivoted to rock on the shaft, a pinion on the shaft connected' to rotate with the driving-gear, a pair of twin pinions journalled on the frame with their teeth in mesh and extending in opposite directions to engage respectively with the drivinggear and driven-gear, a crank-gear journalled on the axis of one of said twin pinions and meshing with the pinion on the shaft, and means engaging the crank-gear to cause it to oscillate the frame to travel the twin pinions circumferentially of their respective gears.

15. A ribbon-breaker for winding machines comprising a shaft, a driving-gear rotatable on said shaft, a pinion on said shaft driven with the driving-gear, a frame having arms pivoted on the shaft, a pair of stud-shafts connecting the arms of said frame, twin pinions journalled on said studshafts in intermeshing relation and meshing respectively with the driving-gear and driven-gear, a crank-gear journalled on one of said stud-shafts in mesh with the pinion on the main shaft and provided with a crankpin, and a fixed arm provided with a :slot engaging said crank-pin whereby the rotation of the crank-gear will oscillate the frame to travel the twin pinions circumferentially of their respective gears.

In testimony whereof we hereunto affix our signatures.

CHARLES H. JONES. ERNEST R. SWANSON. 

